Rotary compressor

ABSTRACT

A rotary compressor ( 100 ) includes a casing ( 1 ), an electric motor ( 2 ) and a compression mechanism ( 3 ), in which the electric motor ( 2 ) includes a stator core ( 21 ) and a rotor core ( 22 ), the compression mechanism ( 3 ) includes an air cylinder assembly ( 31 ) and a main bearing ( 32 ) connected to a side end face of the cylinder assembly ( 31 ) adjacent to the electric motor ( 2 ), the largest distance between a side end face of the stator core ( 21 ) adjacent to the first end wall ( 111 ) and the first end wall ( 111 ) is denoted by Dst, the smallest distance between a side end face of the rotor core ( 22 ) adjacent to the first end wall ( 111 ) and a side end face of a flange portion ( 321 ) of the main bearing ( 32 ) at one side adjacent to the first end wall ( 111 ) is denoted by Drt, in which Dst and Drt satisfy a relationship: 0.335≤Dst/Drt≤0.838.

FIELD

The present disclosure relates to a field of compressor equipment, and more particularly to a rotary compressor.

BACKGROUND

In the related art, it is pointed out that a strong pressure pulsation will be caused when a high pressure gas refrigerant inside a compressor is discharged, and most of noise is generated in a middle cavity of the compressor, then transmitted to an upper cavity through an air hole of a rotor, and eventually transmitted to outside of the compressor by a casing. However, because the high pressure gas refrigerant discharged from a compression pump arrives at the middle cavity firstly, the middle cavity and the upper cavity mainly produce the noise in the range of 1000 Hz-1200 Hz frequency band, which will be extremely ear-piercing in an air conditioning system due to being unable to be eliminated by a sound insulation cotton, thereby adversely affecting the user experience.

SUMMARY

Embodiments of the present disclosure seek to solve at least one of the problems existing in the related art to at least some extent. For that reason, a rotary compressor according to embodiments of the present disclosure is provided, which has low noise, simple and reasonable structure and the like advantages.

The rotary compressor according to embodiments of the present disclosure includes a casing, an electric motor, and a compression mechanism, in which two ends of the casing in an axial direction have a first end wall and a second end wall respectively, the electric motor includes a stator core and a rotor core. In the axial direction of the casing, the largest distance between a side end face of the stator core adjacent to the first end wall and the first end wall is denoted by Dst, the compression mechanism is located at one side of the electric motor far away from the first end wall, the compression mechanism includes an air cylinder assembly and a main bearing. The main bearing is connected to a side end face of the cylinder assembly adjacent to the electric motor, in the axial direction of the casing, the smallest distance between a side end face of the rotor core adjacent to the first end wall and a side end face of a flange portion of the main bearing adjacent to the first end wall is denoted by Drt. In which, Dst and Drt satisfy a relationship: 0.335≤Dst/Drt≤0.838.

By configuring the value of Dst/Drt of the rotary compressor according to embodiments of the present disclosure within a reasonable scope, the noise may be effectively reduced when the rotary compressor is working, thereby the rotary compressor having a simple and reasonable structure, easy assembly, low noise and the like advantages.

According to an embodiment of the present disclosure, the Dst and Drt further satisfy a relationship: 0.568≤Dst/Drt≤0.680.

According to an embodiment of the present disclosure, an air hole is formed on and throughout the rotor core, a central axis of the air hole is parallel to a rotation axis of the rotor core.

According to an embodiment of the present disclosure, the air holes are axisymmetrically distributed about a first diameter of the rotor core, a width D of the air hole in a first diameter direction satisfies a relationship: 0.204 mm≤D≤0.480 mm.

According to an embodiment of the present disclosure, D further satisfies a relationship: 0.404 mm≤D≤0.460 mm.

According to an embodiment of the present disclosure, a contour of a cross section of the air hole is a curve or a combination of a curve and a straight line.

According to an embodiment of the present disclosure, in a rotation axis direction of the rotor core, the cross section of the air hole has the same shape and dimension.

According to an embodiment of the present disclosure, a plurality of air holes are provided and evenly spaced apart from one another along a circumferential direction of the rotor core.

According to an embodiment of the present disclosure, each air hole has the same shape and dimension.

According to an embodiment of the present disclosure, the rotor core is rotatably disposed inside the stator core.

Additional aspects and advantages of embodiments of present disclosure will be given in part in the following descriptions, become apparent in part from the following descriptions, or be learned from the practice of the embodiments of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a sectional view of a rotary compressor according to embodiments of the present disclosure;

FIG. 2 is a schematic view of a rotor core according to an embodiment of the present disclosure from an axial direction;

FIG. 3 is a schematic view of a rotor core according to another embodiment of the present disclosure from an axial direction;

FIG. 4 is a schematic view of a rotor core according to a further embodiment of the present disclosure from an axial direction;

FIG. 5 is a curve diagram showing a relationship between a ratio of Dst/Drt and a noise level according to embodiments of the present disclosure;

FIG. 6 is a curve diagram showing a relationship between a value of D and a noise level according to embodiments of the present disclosure.

REFERENCE NUMERALS

casing 1; first casing 11; first end wall 111; middle casing 12; second casing 13; second end wall 131;

electric motor 2; stator core 21; rotor core 22; air hole 221;

compression mechanism 3; air cylinder assembly 31; main bearing 32; flange portion 321;

crankshaft 4.

DETAILED DESCRIPTION

Reference will be made in detail to embodiments of the present disclosure. The same or similar elements and the elements having same or similar functions are denoted by like reference numerals throughout the descriptions. The embodiments described herein with reference to drawings are explanatory, illustrative, and used to generally understand the present disclosure. The embodiments shall not be construed to limit the present disclosure.

Various embodiments and examples are provided in the following description to implement different structures of the present disclosure. In order to simplify the present disclosure, certain elements and settings will be described. However, these elements and settings are only by way of example and are not intended to limit the present disclosure. In addition, reference numerals may be repeated in different examples in the present disclosure. This repeating is for the purpose of simplification and clarity and does not refer to relations between different embodiments and/or settings. Furthermore, examples of different processes and materials are provided in the present disclosure. However, it would be appreciated by those skilled in the art that other processes and/or materials may be also applied.

A rotary compressor 100 according to embodiments of the present disclosure will be described with reference to FIG. 1-FIG. 6, which may transform a low-temperature and low-pressure refrigerant to a high-temperature and high-pressure refrigerant. In which, the rotary compressor 100 may be configured as a vertical compressor or a horizontal compressor. In the following, the rotary compressor 100 configured as the vertical compressor is used as an example to make the description.

Referring to FIG. 1, the rotary compressor 100 according to embodiments of the present disclosure includes a casing 1, an electric motor 2, a compression mechanism 3 and a crankshaft 4.

In which, two ends of the casing 1 in an axial direction have a first end wall 111 and a second end wall 131 respectively. For example in an embodiment shown in FIG. 1, the casing 1 may include a first casing 11, a middle casing 12 and a second casing 13. The middle casing 12 may be cylindrical in shape, thereby the cylindrical middle casing 12 may define a certain accommodating space therein, facilitating parts (such as the electric motor 2 and the compression mechanism 3 shown in FIG. 1) inside the rotary compressor 100 to be mounted.

Referring to FIG. 1, the first casing 11 (for example, an upper casing shown in FIG. 1) and the second casing 13 (for example, a lower casing shown in FIG. 1) are connected to the two ends of the middle casing 12 in the axial direction. By this way, the first end wall 111 may be configured as a bottom wall of the first casing 11 and the second end wall 131 may be configured as a top wall of the second casing 13.

Further, any one of the first casing 11 and the second casing 13 may be integrated with the middle casing 12. Referring to FIG. 1, the first casing 11 may be integrated with the middle casing 12, thereby the middle casing 12 may be fixed to the second casing 13 when the parts are assembled, facilitating the assembly of the rotary compressor 100 and improving the production efficiency. Certainly, the second casing 13 may be integrated with the middle casing 12, thereby the middle casing 12 may be fixed to the first casing 11 when the parts are assembled, completing the assembly of the rotary compressor 100.

Specifically, the electric motor 2 is disposed in the casing 1 and includes a stator core 21 and a rotor core 22. In the axial direction of the casing 1 (for example, an up-down direction shown in FIG. 1), the largest distance between a side end face of the stator core 21 adjacent to the first end wall 111 and the first end wall 111 is denoted by Dst. For example, in the embodiment shown in FIG. 1, in the up-down direction, the distance between an upper end face of the stator core 21 and the first end wall 111 is Dst. It should be noted that, when the first casing 11 has an irregular form, Dst is the largest distance between the upper end face of the stator core 21 and an inner wall of the first casing 11.

Further, the compression mechanism 3 is disposed in the casing 1 and is located at one side of the electric motor 2 far away from the first end wall 111. For example, in the embodiment shown in FIG. 1, the compression mechanism 3 may be disposed below the electric motor 2, so that the compression mechanism 3 is farther away from the first end wall 111 than the electric motor 2 is, to facilitate installation and fitting between the electric motor 2 and the compression mechanism 3.

Specifically, referring to FIG. 1, the compression mechanism 3 includes an air cylinder assembly 31 and a main bearing 32. The main bearing 32 is connected to a side end face of the cylinder assembly 31 (for example, an upper surface of the cylinder assembly 31 shown in FIG. 1) adjacent to the electric motor 2, in the axial direction of the casing 1 (for example, the un-down direction shown in FIG. 1), the smallest distance between a side end face of the rotor core 22 adjacent to the first end wall 111 and a side end face of an flange portion 321 of the main bearing 32 adjacent to the first end wall 111 is denoted by Drt. For example, in the embodiment shown in FIG. 1, the distance between an upper end face of the rotor core 22 and a top of the flange portion 321 of the main bearing 32 is Drt.

In which, Dst and Drt satisfy a relationship: 0.335≤Dst/Drt≤0.838. Referring to FIG. 5, it should be noted that, a horizontal coordinate in FIG. 5 represents a ratio of Dst/Drt and a vertical coordinate a in FIG. 5 represents a noise OA level when the rotary compressor 100 is working. Specifically, with the increasing of Dst/Drt, the noise OA level of the rotary compressor 100 during operation reduces to a certain extent first and then increases gradually. By the different designs of the ratio of Dst/Drt of the rotary compressor 100, the rotary compressor 100 may produce different noises, for example, when Dst/Drt is equal to 0.4, 0.45, 0.55, 0.6 or 0.75, the working noise of the rotary compressor 100 may be reduced effectively.

It can be seen, by setting the ratio of Dst/Drt of the rotary compressor 100 as: 0.335≤Dst/Drt≤0.838, the working noise of the rotary compressor 100 may be reduced effectively.

In should be noted that, both the electric motor 2 and the compression mechanism 3 may be disposed coaxially with the casing 1, that is to say, a central axis of the crankshaft 4 and a central axis of the casing 1 are coincident, thereby a rotation axis of the rotor core 22 being coincident with the central axis of the casing 1, which means that both a central axis of the main bearing 32 and a central axis of the air cylinder assembly 31 are coincident with the central axis of the casing 1, thus the structure of the rotary compressor 100 being simple and reasonable, and the assembly of the rotary compressor 100 being convenient.

By configuring the value of Dst/Drt of the rotary compressor 100 according to embodiments of the present disclosure within a reasonable scope, the noise may be effectively reduced when the rotary compressor 100 is working, thereby the rotary compressor 100 having a simple and reasonable structure, easy assembly, low noise and the like advantages.

Preferably, Dst and Drt further satisfy a relationship: 0.568≤Dst/Drt≤0.680. For example, when Dst/Drt is equal to 0.58, 0.6 or 0.65, the working noise of the rotary compressor 100 is close to the minimum. It can be seen, by configuring the ratio of Dst/Drt of the rotary compressor 100 as: 0.568≤Dst/Drt≤0.680, the working noise of the rotary compressor 100 may be further reduced.

In some embodiments of the present disclosure, referring to FIG. 1 and FIG. 2, the high-temperature and high-pressure refrigerant discharged from the compression mechanism 3 may be transmitted upwardly, and an air hole 221 is formed on and throughout the rotor core 22, thereby facilitating upward transmission of the high-temperature and high-pressure refrigerant and reducing the noise.

Further, a central axis of the air hole 221 is parallel to the rotation axis of the rotor core 22, for example, in the embodiment shown in FIG. 1, the rotation axis of the rotor core 22 is in the up-down direction, thereby the central axis of the air hole 221 being in the up-down direction as well, thereby further facilitating the upward transmission of the high-temperature and high-pressure refrigerant and further reducing the noise effectively.

In some embodiments of the present disclosure, the air holes 221 are axisymmetrically distributed about a first diameter of the rotor core 22, a width D of the air hole 221 in the first diameter direction satisfies: 0.204 mm≤D≤0.480 mm. For example, in an embodiment shown in FIG. 2, the air holes 221 may be symmetrically disposed about the first diameter k of the rotor core 22, and the width of the air hole 221 in the first diameter k is denoted by D. Referring to FIG. 6, it should be noted that, a horizontal coordinate in FIG. 6 represents a value of D and a vertical coordinate a in FIG. 6 represents a noise OA level when the rotary compressor 100 is working. Specifically, with the increasing of the D, the working noise of the rotary compressor 100 gradually reduces to a certain extent first and then increases gradually. By the different designs of the value of D of the air hole 221 of the rotary compressor 100, the rotary compressor 100 may produce different noises, for example, when D is equal to 0.25 mm, 0.35 mm or 0.41 mm, the working noise of the rotary compressor 100 may be reduced effectively.

It can be seen, by configuring the value of D of the air hole 221 of the rotary compressor 100 as: 0.204 mm≤D≤0.480 mm, the working noise of the rotary compressor 100 may be reduced effectively.

Preferably, D further satisfies a relationship: 0.404 mm≤D≤0.460 mm, fox example when D is equal to 0.41 mm, 0.43 mm or 0.45 mm, the working noise of the rotary compressor 100 is close to the minimum. It can be seen, by configuring the value of D of the air hole 221 of the rotary compressor 100 as: 0.404 mm≤D≤0.460 mm, the working noise of the rotary compressor 100 may be further reduced.

In some embodiments of the present disclosure, a contour of a cross section of the air hole 221 may be a curve or a combination of a curve and a straight line. For example, the cross section of the air hole 221 may be configured in the shape of a hollow curve (as shown in FIG. 2), or a circle (as shown in FIG. 3), as well as a rounded rectangle (as shown in FIG. 4), thereby facilitating circulation of the high-temperature and high-pressure refrigerant and reducing the working noise of the rotary compressor 100. Certainly, the present disclosure is not limited to this, the cross section of the air hole 221 may be configured in the shape of other curves or combinations of straight lines and curves, so as to meet the actual use requirements better.

In some embodiments of the present disclosure, in the rotation axis direction of the rotor core 22 (for example the up-down direction as shown in FIG. 1), the cross section of the air hole 221 has the same shape and dimension, thereby on one hand facilitating the process of the air hole 221, reducing the production process complexity of the rotary compressor 100, and on the other hand facilitating homogeneous circulation of the high-temperature and high-pressure refrigerant through the air hole 221, further reducing the working noise of the rotary compressor 100.

In some embodiments of the present disclosure, referring to FIG. 2, a plurality of air holes 221 may be provided and evenly spaced apart from one another along the circumferential direction of the rotor core 22, that is to say, the plurality of air holes 221 are evenly spaced apart from one another along the circumferential direction of the rotor core 22, thereby facilitating the process of the air hole 221 and the circulation of the high-temperature and high-pressure refrigerant.

Further, referring to FIG. 2 to FIG. 4, each air hole 221 has the same shape and dimension, thereby facilitating the process of the air holes 221, improving the homogeneous circulation of the high-temperature and high-pressure refrigerant, further reducing the working noise of the rotary compressor 100.

In some embodiments of the present disclosure, referring to FIG. 1, the rotor core 22 may be rotatably disposed inside the stator core 21. Specifically, a peripheral wall of the stator core 21 may be fixed to an inner circumferential wall of the casing 1, the rotor core 22 may be connected with a thermal sleeve of the crankshaft 4, thereby improving the fitting stability between the electric motor 2 and the compression mechanism 3 effectively, and facilitating the assembly of the rotary compressor 100. Certainly, the present disclosure is not limited to this, the rotor core 22 may be rotatably disposed outside the stator core 21 as well.

In addition, the other components, working principles and operation manners of the rotary compressor according to embodiments of the present disclosure are known to those skilled in the art, which will not be described herein. In the specification, it is to be understood that terms such as “central,” “longitudinal,” “lateral,” “length,” “width,” “thickness,” “upper,” “lower,” “front,” “rear,” “left,” “right,” “vertical,” “horizontal,” “top,” “bottom,” “inner,” “outer,” “clockwise,” and “counterclockwise” should be construed to refer to the orientation as then described or as shown in the drawings under discussion. These relative terms are for convenience of description and do not require that the present invention be constructed or operated in a particular orientation.

In addition, terms such as “first” and “second” are used herein for purposes of description and are not intended to indicate or imply relative importance or significance or to imply the number of indicated technical features. Thus, the feature defined with “first” and “second” may comprise one or more of this feature. In the description of the present invention, “a plurality of” means two or more than two, unless specified otherwise.

In the present invention, unless specified or limited otherwise, the terms “mounted,” “connected,” “coupled,” “fixed” and the like are used broadly, and may be, for example, fixed connections, detachable connections, or integral connections; may also be mechanical or electrical connections; may also be direct connections or indirect connections via intervening structures; may also be inner communications of two elements, which can be understood by those skilled in the art according to specific situations.

In the present invention, unless specified or limited otherwise, a structure in which a first feature is “on” or “below” a second feature may include an embodiment in which the first feature is in direct contact with the second feature, and may also include an embodiment in which the first feature and the second feature are not in direct contact with each other, but are contacted via an additional feature formed therebetween. Furthermore, a first feature “on,” “above,” or “on top of” a second feature may include an embodiment in which the first feature is right or obliquely “on,” “above,” or “on top of” the second feature, or just means that the first feature is at a height higher than that of the second feature; while a first feature “below,” “under,” or “on bottom of” a second feature may include an embodiment in which the first feature is right or obliquely “below,” “under,” or “on bottom of” the second feature, or just means that the first feature is at a height lower than that of the second feature.

Reference throughout this specification to “an embodiment,” “some embodiments,” “one embodiment”, “another example,” “an example,” “a specific example,” or “some examples,” means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. Thus, the appearances of the phrases such as “in some embodiments,” “in one embodiment”, “in an embodiment”, “in another example,” “in an example,” “in a specific example,” or “in some examples,” in various places throughout this specification are not necessarily referring to the same embodiment or example of the present disclosure. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

Although explanatory embodiments have been shown and described, it would be appreciated by those skilled in the art that the above embodiments cannot be construed to limit the present disclosure, and changes, alternatives, and modifications can be made in the embodiments without departing from spirit, principles and scope of the present disclosure. 

1. A rotary compressor comprising: a casing, two ends of the casing in an axial direction having a first end wall and a second end wall respectively; an electric motor disposed in the casing and comprising a stator core and a rotor core, wherein in the axial direction of the casing, the largest distance between a side end face of the stator core adjacent to the first end wall and the first end wall is denoted by Dst; a compression mechanism disposed in the casing and located at one side of the electric motor far away from the first end wall, the compression mechanism comprising an air cylinder assembly and a main bearing, the main bearing being connected to a side end face of the cylinder assembly adjacent to the electric motor, wherein in the axial direction of the casing, the smallest distance between a side end face of the rotor core adjacent to the first end wall and a side end face of a flange portion of the main bearing adjacent to the first end wall is denoted by Drt; wherein, Dst and Drt satisfy a relationship: 0.335≤Dst/Drt≤0.838.
 2. The rotary compressor according to claim 1, wherein Dst and Drt further satisfy a relationship: 0.568≤Dst/Drt≤0.680.
 3. The rotary compressor according to claim 1, wherein an air hole is formed on and throughout the rotor core and a central axis of the air hole is parallel to a rotation axis of the rotor core.
 4. The rotary compressor according to claim 3, wherein the air holes are axisymmetrically distributed about a first diameter of the rotor core and a width D of the air hole in a first diameter direction satisfies a relationship: 0.204 mm≤D≤0.480 mm.
 5. The rotary compressor according to claim 4, wherein D further satisfies a relationship: 0.404 mm≤D≤0.460 mm.
 6. The rotary compressor according to claim 3, wherein a contour of a cross section of the air hole is a curve or a combination of a curve and a straight line.
 7. The rotary compressor according to claim 3, wherein in a rotation axis direction of the rotor core, the cross section of the air hole has the same shape and dimension.
 8. The rotary compressor according to claim 3, wherein a plurality of air holes are provided and evenly spaced apart from one another along a circumferential direction of the rotor core.
 9. The rotary compressor according to claim 8, wherein each air hole has the same shape and dimension.
 10. The rotary compressor according to claim 1, wherein the rotor core is rotatably disposed inside the stator core.
 11. The rotary compressor according to claim 4, wherein a contour of a cross section of the air hole is a curve or a combination of a curve and a straight line.
 12. The rotary compressor according to claim 5, wherein a contour of a cross section of the air hole is a curve or a combination of a curve and a straight line.
 13. The rotary compressor according to claim 4, wherein in a rotation axis direction of the rotor core, the cross section of the air hole has the same shape and dimension.
 14. The rotary compressor according to claim 5, wherein in a rotation axis direction of the rotor core, the cross section of the air hole has the same shape and dimension.
 15. The rotary compressor according to claim 6, wherein in a rotation axis direction of the rotor core, the cross section of the air hole has the same shape and dimension.
 16. The rotary compressor according to claim 4, wherein a plurality of air holes are provided and evenly spaced apart from one another along a circumferential direction of the rotor core.
 17. The rotary compressor according to claim 5, wherein a plurality of air holes are provided and evenly spaced apart from one another along a circumferential direction of the rotor core.
 18. The rotary compressor according to claim 6, wherein a plurality of air holes are provided and evenly spaced apart from one another along a circumferential direction of the rotor core.
 19. The rotary compressor according to claim 7, wherein a plurality of air holes are provided and evenly spaced apart from one another along a circumferential direction of the rotor core.
 20. The rotary compressor according to claim 2, wherein the rotor core is rotatably disposed inside the stator core. 